JP2001500823A - Planetary transmission for vehicles - Google Patents

Planetary transmission for vehicles

Info

Publication number
JP2001500823A
JP2001500823A JP11506997A JP50699799A JP2001500823A JP 2001500823 A JP2001500823 A JP 2001500823A JP 11506997 A JP11506997 A JP 11506997A JP 50699799 A JP50699799 A JP 50699799A JP 2001500823 A JP2001500823 A JP 2001500823A
Authority
JP
Japan
Prior art keywords
planet carrier
planetary transmission
planetary
housing
static housing
Prior art date
Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.)
Pending
Application number
JP11506997A
Other languages
Japanese (ja)
Other versions
JP2001500823A5 (en
Inventor
キングストン，ティム
Original Assignee
ボルボ コンストラクション イクィプメント コンポネンツ アーベー
Priority date (The priority date is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the date listed.)
Filing date
Publication date
Family has litigation
First worldwide family litigation filed litigation Critical https://patents.darts-ip.com/?family=20407781&utm_source=google_patent&utm_medium=platform_link&utm_campaign=public_patent_search&patent=JP2001500823(A) "Global patent litigation dataset” by Darts-ip is licensed under a Creative Commons Attribution 4.0 International License.
Application filed by ボルボ コンストラクション イクィプメント コンポネンツ アーベー filed Critical ボルボ コンストラクション イクィプメント コンポネンツ アーベー
Publication of JP2001500823A publication Critical patent/JP2001500823A/en
Publication of JP2001500823A5 publication Critical patent/JP2001500823A5/ja
Pending legal-status Critical Current

Links

Classifications

    • B—PERFORMING OPERATIONS; TRANSPORTING
    • B60—VEHICLES IN GENERAL
    • B60K—ARRANGEMENT OR MOUNTING OF PROPULSION UNITS OR OF TRANSMISSIONS IN VEHICLES; ARRANGEMENT OR MOUNTING OF PLURAL DIVERSE PRIME-MOVERS IN VEHICLES; AUXILIARY DRIVES FOR VEHICLES; INSTRUMENTATION OR DASHBOARDS FOR VEHICLES; ARRANGEMENTS IN CONNECTION WITH COOLING, AIR INTAKE, GAS EXHAUST OR FUEL SUPPLY OF PROPULSION UNITS IN VEHICLES
    • B60K17/00—Arrangement or mounting of transmissions in vehicles
    • B60K17/04—Arrangement or mounting of transmissions in vehicles characterised by arrangement, location, or kind of gearing
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16D—COUPLINGS FOR TRANSMITTING ROTATION; CLUTCHES; BRAKES
    • F16D65/00—Parts or details
    • F16D65/38—Slack adjusters
    • F16D65/40—Slack adjusters mechanical
    • F16D65/52—Slack adjusters mechanical self-acting in one direction for adjusting excessive play
    • F16D65/54—Slack adjusters mechanical self-acting in one direction for adjusting excessive play by means of direct linear adjustment
    • B—PERFORMING OPERATIONS; TRANSPORTING
    • B60—VEHICLES IN GENERAL
    • B60K—ARRANGEMENT OR MOUNTING OF PROPULSION UNITS OR OF TRANSMISSIONS IN VEHICLES; ARRANGEMENT OR MOUNTING OF PLURAL DIVERSE PRIME-MOVERS IN VEHICLES; AUXILIARY DRIVES FOR VEHICLES; INSTRUMENTATION OR DASHBOARDS FOR VEHICLES; ARRANGEMENTS IN CONNECTION WITH COOLING, AIR INTAKE, GAS EXHAUST OR FUEL SUPPLY OF PROPULSION UNITS IN VEHICLES
    • B60K17/00—Arrangement or mounting of transmissions in vehicles
    • B60K17/04—Arrangement or mounting of transmissions in vehicles characterised by arrangement, location, or kind of gearing
    • B60K17/043—Transmission unit disposed in on near the vehicle wheel, or between the differential gear unit and the wheel
    • B60K17/046—Transmission unit disposed in on near the vehicle wheel, or between the differential gear unit and the wheel with planetary gearing having orbital motion
    • B—PERFORMING OPERATIONS; TRANSPORTING
    • B60—VEHICLES IN GENERAL
    • B60T—VEHICLE BRAKE CONTROL SYSTEMS OR PARTS THEREOF; BRAKE CONTROL SYSTEMS OR PARTS THEREOF, IN GENERAL; ARRANGEMENT OF BRAKING ELEMENTS ON VEHICLES IN GENERAL; PORTABLE DEVICES FOR PREVENTING UNWANTED MOVEMENT OF VEHICLES; VEHICLE MODIFICATIONS TO FACILITATE COOLING OF BRAKES
    • B60T1/00—Arrangements of braking elements, i.e. of those parts where braking effect occurs specially for vehicles
    • B60T1/02—Arrangements of braking elements, i.e. of those parts where braking effect occurs specially for vehicles acting by retarding wheels
    • B60T1/06—Arrangements of braking elements, i.e. of those parts where braking effect occurs specially for vehicles acting by retarding wheels acting otherwise than on tread, e.g. employing rim, drum, disc, or transmission or on double wheels
    • B60T1/062—Arrangements of braking elements, i.e. of those parts where braking effect occurs specially for vehicles acting by retarding wheels acting otherwise than on tread, e.g. employing rim, drum, disc, or transmission or on double wheels acting on transmission parts
    • B—PERFORMING OPERATIONS; TRANSPORTING
    • B60—VEHICLES IN GENERAL
    • B60T—VEHICLE BRAKE CONTROL SYSTEMS OR PARTS THEREOF; BRAKE CONTROL SYSTEMS OR PARTS THEREOF, IN GENERAL; ARRANGEMENT OF BRAKING ELEMENTS ON VEHICLES IN GENERAL; PORTABLE DEVICES FOR PREVENTING UNWANTED MOVEMENT OF VEHICLES; VEHICLE MODIFICATIONS TO FACILITATE COOLING OF BRAKES
    • B60T1/00—Arrangements of braking elements, i.e. of those parts where braking effect occurs specially for vehicles
    • B60T1/02—Arrangements of braking elements, i.e. of those parts where braking effect occurs specially for vehicles acting by retarding wheels
    • B60T1/06—Arrangements of braking elements, i.e. of those parts where braking effect occurs specially for vehicles acting by retarding wheels acting otherwise than on tread, e.g. employing rim, drum, disc, or transmission or on double wheels
    • B60T1/065—Arrangements of braking elements, i.e. of those parts where braking effect occurs specially for vehicles acting by retarding wheels acting otherwise than on tread, e.g. employing rim, drum, disc, or transmission or on double wheels employing disc
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16D—COUPLINGS FOR TRANSMITTING ROTATION; CLUTCHES; BRAKES
    • F16D55/00—Brakes with substantially-radial braking surfaces pressed together in axial direction, e.g. disc brakes
    • F16D55/24—Brakes with substantially-radial braking surfaces pressed together in axial direction, e.g. disc brakes with a plurality of axially-movable discs, lamellae, or pads, pressed from one side towards an axially-located member
    • F16D55/26—Brakes with substantially-radial braking surfaces pressed together in axial direction, e.g. disc brakes with a plurality of axially-movable discs, lamellae, or pads, pressed from one side towards an axially-located member without self-tightening action
    • F16D55/36—Brakes with a plurality of rotating discs all lying side by side
    • F16D55/40—Brakes with a plurality of rotating discs all lying side by side actuated by a fluid-pressure device arranged in or one the brake
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16D—COUPLINGS FOR TRANSMITTING ROTATION; CLUTCHES; BRAKES
    • F16D65/00—Parts or details
    • F16D65/38—Slack adjusters
    • F16D65/72—Slack adjusters hydraulic
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16H—GEARING
    • F16H3/00—Toothed gearings for conveying rotary motion with variable gear ratio or for reversing rotary motion
    • F16H3/44—Toothed gearings for conveying rotary motion with variable gear ratio or for reversing rotary motion using gears having orbital motion
    • F16H3/46—Gearings having only two central gears, connected by orbital gears
    • F16H3/48—Gearings having only two central gears, connected by orbital gears with single orbital gears or pairs of rigidly-connected orbital gears
    • F16H3/52—Gearings having only two central gears, connected by orbital gears with single orbital gears or pairs of rigidly-connected orbital gears comprising orbital spur gears
    • F16H3/54—Gearings having only two central gears, connected by orbital gears with single orbital gears or pairs of rigidly-connected orbital gears comprising orbital spur gears one of the central gears being internally toothed and the other externally toothed
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16H—GEARING
    • F16H57/00—General details of gearing
    • F16H57/08—General details of gearing of gearings with members having orbital motion
    • F16H57/10—Braking arrangements
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16D—COUPLINGS FOR TRANSMITTING ROTATION; CLUTCHES; BRAKES
    • F16D55/00—Brakes with substantially-radial braking surfaces pressed together in axial direction, e.g. disc brakes
    • F16D2055/0004—Parts or details of disc brakes
    • F16D2055/0058—Fully lined, i.e. braking surface extending over the entire disc circumference
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16D—COUPLINGS FOR TRANSMITTING ROTATION; CLUTCHES; BRAKES
    • F16D2121/00—Type of actuator operation force
    • F16D2121/02—Fluid pressure
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16H—GEARING
    • F16H1/00—Toothed gearings for conveying rotary motion
    • F16H1/28—Toothed gearings for conveying rotary motion with gears having orbital motion
    • Y—GENERAL TAGGING OF NEW TECHNOLOGICAL DEVELOPMENTS; GENERAL TAGGING OF CROSS-SECTIONAL TECHNOLOGIES SPANNING OVER SEVERAL SECTIONS OF THE IPC; TECHNICAL SUBJECTS COVERED BY FORMER USPC CROSS-REFERENCE ART COLLECTIONS [XRACs] AND DIGESTS
    • Y10—TECHNICAL SUBJECTS COVERED BY FORMER USPC
    • Y10T—TECHNICAL SUBJECTS COVERED BY FORMER US CLASSIFICATION
    • Y10T74/00—Machine element or mechanism
    • Y10T74/19—Gearing
    • Y10T74/19545—Central driving shaft in axle

Landscapes

  • Engineering & Computer Science (AREA)
  • General Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • Transportation (AREA)
  • Chemical & Material Sciences (AREA)
  • Combustion & Propulsion (AREA)
  • Braking Arrangements (AREA)
  • General Details Of Gearings (AREA)
  • Retarders (AREA)
  • Motor Power Transmission Devices (AREA)
  • Arrangement Of Transmissions (AREA)
  • Friction Gearing (AREA)
  • Sampling And Sample Adjustment (AREA)

Abstract

(57)【要約】 本発明は、少なくとも１個の遊星歯車（４）が装着される遊星キャリヤ（２）、車両用車輪（２５）のために配列され、前記遊星キャリヤ（２）に接続されるハブ（１６）、および車両に接続され、内部にはハブ（１６）が装着される静的ハウジング（２８）から成る車両用の遊星変速装置に関する。摩擦ブレーキ（３４）は、前記遊星キャリヤ（２）の外周縁部に配列され、前記静的ハウジング（２８）に関連して前記遊星キャリヤ（２）の回転の制動を行うことにある。前記ハブ（１６）と前記遊星キャリヤ（２）はスプライン接続（１４，２１）によって内部結合される。１実施例によれば、外側歯車環（３０’）は少なくとも１個の遊星歯車（４）と相互作用するように配列され、該外側歯車環（３０’）は第２スプライン接続（４２，７４）によって前記静的ハウジング（２８）に接続される。 SUMMARY OF THE INVENTION The present invention provides a planetary carrier (2) on which at least one planetary gear (4) is mounted, arranged for a vehicle wheel (25) and connected to said planetary carrier (2). A planetary transmission for a vehicle comprising a hub (16) connected to the vehicle and a static housing (28) connected to the vehicle and having the hub (16) mounted therein. A friction brake (34) is arranged on the outer peripheral edge of the planet carrier (2) and is for braking the rotation of the planet carrier (2) in relation to the static housing (28). The hub (16) and the planet carrier (2) are interconnected by spline connections (14, 21). According to one embodiment, the outer gear ring (30 ') is arranged to interact with at least one planetary gear (4), said outer gear ring (30') being connected to the second spline connection (42,74). ) Is connected to said static housing (28).

Description

【発明の詳細な説明】 車両用の遊星変速装置 本発明は、少なくとも１つの遊星歯車が装着される遊星キャリヤ、車輪のため に配列され、前記遊星キャリヤに接続されるハブ、車両に接続され、内部には前 記ハブが装着される静的ハウジング、および前記遊星キャリヤの外周縁部に配列 され、前記静的ハウジングに関連して前記遊星キャリヤの回転の制動をすること にある摩擦ブレーキから成る車両用の遊星変速装置に関する。 車輪と関連して遊星変速装置を配列することは以前から知られている。車両の 駆動シャフトには前記遊星変速装置用の内側太陽歯車が配設され、該遊星変速装 置を取囲んでいる静的ハウジングには外側歯車環が提供されている。前記太陽歯 車と前記歯車環は、１つの遊星キャリヤ上に配列される遊星歯車と相互作用をす る。前記遊星キャリヤは、前記静的ハウジング内に装着されるハブに接続され、 車両用の車輪は、車輪ボルトを使って該ハブ上に装着される。車両用の車輪と関 連して遊星変速装置を配列することにより、駆動シャフトから車輪へのトルクは 増大され得る。車両を制動するために、摩擦ディスクは前記遊星キャリヤの外周 縁上に配列され、該遊星キャリヤは前記静的ハウジング内に配列されるディスク 板と相互作用をする。 既知の遊星変速装置の構成は、例えば、より堅剛なハブ軸受配列を必要とし、 結果として軸方向により長いハブを必要とする産業機械のような大型で、重量あ る車両には不適切である。しかし、このことが遊星キャリヤとハブとの間の接続 に対する多大な要求へと結びついていて、それと同時に、遊星変速装置全体を出 来る限り小型に保持することが望まれている。 本発明の目的は、上記の問題を取除き、また、出来る限り小型な構成が得られ る序文に記載の型の遊星変速装置を生産することにある。 更に、本発明の目的は、比較的少ない数の構成部品から成り、製造するのが簡 単で、安価な遊星変速装置を生産することにある。 本発明によれば、これは、ハブと遊星キャリヤが第１スプライン接続によって 内部連結されるという事実によって達成される。 この種の遊星変速装置は小型であり、既知の構成のものよりも相当大きな力を 吸 収するように寸法付けられているという事実にも係わらず既知の遊星変速装置よ りも少ない部品から成っている。 本発明は、２つの実施例を示す添付図面を参照にしながら以下でより詳細に説 明される。図１は、本発明の第１実施例による遊星変速装置の側断面図を示す。 図２は、本発明の第２実施例による遊星変速装置の側断面図を示す。 図１では、参照番号１は、遊星変速装置１が遊星キャリヤ２から成る車両用の 遊星変速装置を指示し、該遊星キャリア２上には多くの遊星歯車４が配列される 。車両のエンジン或はギアボックス（不図示）から１本の駆動シャフト６は延在 し、その外端部８は遊星変速装置１のための１つの内側太陽歯車１０から成り、 該内側太陽歯車１０は遊星キャリヤ２上の前記遊星歯車４と相互作用をする。図 １の第１実施例によれば、前記遊星歯車４の数は３個であるが、その数を２個、 ４個或はそれ以上にすることも可能である。 車両という用語は、道路上を走行するための車両および、例えば、森林のよう な道路以外の場所における走行を目的とする車両の両方の車両の意味に使われる 。この種の車両は、ダンプトラック、ホイールローダ、掘削機或は他の産業機械 であり得る。 遊星キャリヤ２はスプライン１４が配設されている貫通孔１２から成る。該貫 通孔１２の中央線１５は、遊星キャリヤ２の回転軸と一致している。第１端部１ ８においてスプライン２１と共にジャーナル２０からなるハブ１６は、遊星キャ リヤ２の該貫通孔１２内で配列され、その結果、遊星キャリヤ２に放射方向に接 続される。板１９はスクリュウ２３を使いハブ１６に接続され、該ハブ１６が遊 星キャリヤ２に軸方向に接続されるのを確実なものとする。前記ハブ１６は第２ 端部２２において車両用の車輪２５のための固定配列２４から成る。 前記ハブ１６は、車両に接続される静的ハウジング２８内でころ軸受２６を使 って装着される。従って、前記ハブ１６は前記ハウジング２８に関連して回転す る。ハウジング２８内に配列されるのは遊星変速装置１のための１つの外側歯車 環３０であり、該歯車環３０は遊星キャリヤ２上で前記遊星歯車４と相互作用を することを目的とする。前記歯車環３０は下記で説明される１つの摩擦ブレーキ ３４ための１枚の第１圧力板３２へ接続される。 前記摩擦ブレーキ３４は遊星キャリヤ２の周縁部上に配列される摩擦ディスク ３６の集合から成る。図示の第１実施例によれば、前記摩擦ディスク３６の数は ８個になっているが、この数は任意であることが可能である。前記摩擦ディスク ３６は、遊星キャリヤ２の周縁部上に配列されるスプライン３８上で軸方向に変 位可能である。前記摩擦ディスク３６は遊星キャリヤ２上で円周方向にロックさ れる。 ディスク板４０の集合は、ハウジング２８内でスプライン４２上に配列される 。前記ディスク板４０は軸方向に変位可能であるが、ハウジング２８に関して円 周方向にロックされる。前記ディスク板４０の数は前記摩擦ディスク３６の数と 等しいことが好ましい。選択的に、前記ディスク板４０が遊星キャリヤ２の周縁 部上に配列され、前記摩擦ディスク３６がハウジング２８内に配列され得る。前 記ディスク板は、例えば、金属、プラスチック或はカーボンファイバから作られ 得る。他の材料を使うことも可能である。 遊星キャリヤ２の回転が制動され、よって車両の動きが制動される時、１枚の 第２圧力板４４は前記摩擦ディスク３６を圧縮し、前記ディスク板４０は前記第 １圧力板３２を圧縮するように配列されている。前記第２圧力板４４は、該圧力 板４４に沿って分布される多数の油圧ピストン４６によって軸方向に変位され得 る。前記油圧ピストン４６は、該油圧ピストン４６に作用する圧力下にある油圧 流体を使って前記第２圧力板４４を軸方向に変位させる。前記油圧流体はハウジ ング２８内に配列される１本の環状導管４８内に含まれる。前記油圧流体は、口 金５０とハウジング２８内の穴５１を通じて前記環状導管４８へと給送される。 前記第１圧力板３２と前記第２圧力板４４との間に配列される１つ或はそれ以上 の螺旋状スプリングは、制動後は前記油圧ピストン４６を初期位置に戻す。 前記第１圧力板３２と前記第２圧力板４４のそれぞれ並びに前記摩擦ディスク ３６と前記ディスク板４０は環状であることが好ましいが、それらはまた、遊星 キャリヤ２の中央線１５の回りで円形に区分状に配列され得る。 図１に示す第１実施例によれば、前記油圧ピストン４６には、前記摩擦ディス ク３６が摩耗するため該油圧ピストン４６の初期位置を調整する自己調整部材５ ２が選択的に提供される。前記自己調整部材５２は、ハウジング２８内で片側閉 塞孔５４内で適合されるグリップと共に配列されるスリーブ５３から成る。前記 スリー ブ５３を通じて延在する１つのピン５６は、第１端部５８では油圧ピストン４６ に接続され、第２端部６０では該ピンにはヘッド６２が提供されており、該ヘッ ド６２は前記スリーブ５３の端部表面６６に対し押し付けるための軸受表面６４ を有する。前記摩擦ディスク３６が摩耗するため、該摩擦ディスク３６と前記デ ィスク板４０とを前記第１圧力板３２に対して圧縮するには、前記油圧ピストン ４６はより長い距離を移動しなければならなず、その結果、より大量の油圧流体 が必要とされる。この問題を克服するために、前記油圧ピストン４６に作用する 油圧流体からの力が、前記ピン５６のヘッド６２を使って、前記スリーブ５３を 前記片側閉塞孔５４内で変位させ新しい位置を占めるように、該スリーブ５３と 該片側閉塞孔５４との間のグリップは適合される。しかし、前記螺旋状スプリン グ４９の力が前記スリーブ５３を前記片側閉塞孔５４内で変位させないように、 該スリーブ５３と該片側閉塞孔５４の間のグリップは適合され、このことは前記 油圧ピストン４６が戻りストローク後は新たな初期位置を占めることを意味して いる。 １選択肢として、センサ６８もまたハウジング１８内に配列されることであり 、該センサは遊星キャリヤ２の回転速度を感知することで車両速度も感知する。 前記センサ６８は、前記第１圧力板３２でハウジング２８の穴７０内に適切に配 列され、該センサは遊星キャリヤ２の周縁部上のスプライン３８を向いており、 該スプライン上に前記第１摩擦ディスク３６は配列される。それから、前記セン サ６８は前記スプライン３８の棒がどれくらい速く該センサ６８を通過するのか を感知し、その速度は遊星キャリヤ２の回転速度に比例している。前記センサ６ ８の感知精度を高めるために、遊星キャリヤ２には、前記第１摩擦ディスク３６ が配列されている該スプライン３８の隣により細かい間隔で歯又はスプラインが 選択的に配設され得る。 図２には、本発明による第２実施例が示されている。この第２実施例による遊 星変速装置は、ハウジング２８内で形成される前記スプライン４２と係合するよ う配列される１つの外側歯車環３０’から成る。前記スプライン４２の高さは、 前記歯車環３０’と相互作用する部分では、該歯車環３０’のための１つの係止 或は軸受表面を形成するために減少されている。前記外側歯車環３０’には、第 ２スプライン接続を形成するようハウジング２８内で前記スプライン４２と係合 するスプラ イン７４が外側の周縁部上に配設される。 前記歯車環３０’は、前記摩擦ディスク３６と前記摩擦ブレーキ３４を形成す る前記ディスク板４０とのための１枚の第１圧力板３２’を形成する。前記摩擦 ブレーキ３４は、管７２を使い冷却装置（不図示）を通じて循環される流体内に おいて動作するのが好ましい。 図２には、自己調整部材５２’が示されている。この自己調整部材５２’は、 摩擦ディスク３６が摩耗するため油圧ピストン４６’の初期位置を調整する。図 ２に関連する上記特徴を別にすれば、図２による遊星変速装置の部分の構成は、 本質的には、図１の遊星変速装置と関連する記載の部分の構成と一致している。DETAILED DESCRIPTION OF THE INVENTION                           Planetary transmission for vehicles   The present invention relates to a planet carrier, wheels on which at least one planet gear is mounted. A hub connected to the planet carrier, connected to the vehicle, A static housing on which the hub is mounted, and an array on an outer peripheral edge of the planet carrier. Braking the rotation of the planet carrier in relation to the static housing A planetary transmission for a vehicle comprising a friction brake.   The arrangement of planetary transmissions in connection with wheels has been known for some time. Vehicle An inner sun gear for the planetary transmission is disposed on the drive shaft. An outer gear ring is provided in the static housing surrounding the device. The sun teeth The wheel and the gear ring interact with planetary gears arranged on one planet carrier. You. The planet carrier is connected to a hub mounted within the static housing; Vehicle wheels are mounted on the hub using wheel bolts. Vehicle wheels and wheels By arranging the planetary transmission in series, the torque from the drive shaft to the wheels is reduced Can be increased. In order to brake the vehicle, the friction disc is placed on the outer circumference of the planet carrier. A disk arranged on the edge, wherein the planet carrier is arranged in the static housing Interacts with the board.   Known planetary transmission configurations, for example, require a more rigid hub bearing arrangement, As a result, large, heavyweight machines such as industrial machines that require longer axial hubs. Not suitable for vehicles However, this is the connection between the planet carrier and the hub. And at the same time, launch the entire planetary transmission. It is desired to keep it as small as possible.   An object of the present invention is to eliminate the above-mentioned problems and to obtain a configuration as small as possible. To produce a planetary transmission of the type described in the introduction.   Furthermore, the object of the invention consists of a relatively small number of components and is simple to manufacture. It is simply to produce an inexpensive planetary transmission.   According to the invention, this means that the hub and the planet carrier are connected by a first spline connection. Achieved by the fact that they are interconnected.   This type of planetary transmission is small and can apply significantly more force than known configurations. Sucking Known planetary transmission, despite the fact that it is dimensioned to accommodate It is made up of less components.   The invention is explained in more detail below with reference to the accompanying drawings, which show two embodiments. Will be revealed. FIG. 1 is a side sectional view of a planetary transmission according to a first embodiment of the present invention. FIG. 2 is a side sectional view of a planetary transmission according to a second embodiment of the present invention.   In FIG. 1, reference numeral 1 designates a vehicle for which the planetary transmission 1 comprises a planetary carrier 2. Instructs a planetary transmission, on which a number of planetary gears 4 are arranged. . One drive shaft 6 extends from the vehicle engine or gearbox (not shown) And its outer end 8 comprises one inner sun gear 10 for the planetary transmission 1, The inner sun gear 10 interacts with the planet gear 4 on the planet carrier 2. Figure According to the first embodiment, the number of the planetary gears 4 is three, but the number is two. It is possible to have four or more.   The term vehicle refers to vehicles for driving on roads and, for example, Used to mean both vehicles intended to travel on non-roads . Such vehicles include dump trucks, wheel loaders, excavators or other industrial machines Can be   The planet carrier 2 comprises a through hole 12 in which a spline 14 is arranged. The uki The center line 15 of the through hole 12 coincides with the rotation axis of the planet carrier 2. First end 1 In FIG. 8, the hub 16 consisting of the journal 20 together with the spline 21 is Arranged in the through hole 12 of the rear 2, as a result, it comes into radial contact with the planet carrier 2. Continued. The plate 19 is connected to the hub 16 using a screw 23, and the hub 16 is It is ensured that it is connected to the star carrier 2 in the axial direction. The hub 16 is a second At the end 22, it consists of a fixed arrangement 24 for a vehicle wheel 25.   The hub 16 uses a roller bearing 26 in a static housing 28 connected to the vehicle. Is attached. Thus, the hub 16 rotates relative to the housing 28. You. Arranged in the housing 28 is one external gear for the planetary transmission 1 A ring 30 which interacts with the planetary gear 4 on the planet carrier 2; The purpose is to do. The gear ring 30 is a friction brake described below. 34 is connected to one first pressure plate 32.   The friction brake 34 is a friction disk arranged on the periphery of the planetary carrier 2. It consists of 36 sets. According to the first embodiment shown, the number of said friction disks 36 is Although there are eight, this number can be arbitrary. The friction disc Reference numeral 36 denotes an axially changing spline 38 arranged on the periphery of the planet carrier 2. Is possible. The friction disc 36 is circumferentially locked on the planet carrier 2. It is.   The set of disk plates 40 is arranged on the splines 42 in the housing 28. . The disk plate 40 is axially displaceable, but is circular with respect to the housing 28. Locked in the circumferential direction. The number of the disc plates 40 is the same as the number of the friction discs 36. Preferably, they are equal. Optionally, said disk plate 40 is located on the periphery of the planet carrier 2. The friction disks 36 may be arranged in the housing 28. Previous The disc is made of, for example, metal, plastic or carbon fiber. obtain. Other materials can be used.   When the rotation of the planet carrier 2 is braked and thus the movement of the vehicle is braked, one The second pressure plate 44 compresses the friction disc 36, and the disc plate 40 One pressure plate 32 is arranged to compress. The second pressure plate 44 applies the pressure Can be axially displaced by a number of hydraulic pistons 46 distributed along the plate 44; You. The hydraulic piston 46 has a hydraulic pressure under a pressure acting on the hydraulic piston 46. The second pressure plate 44 is displaced in the axial direction using a fluid. The hydraulic fluid is a housing Included in a single annular conduit 48 arranged in the ring 28. The hydraulic fluid is It is fed into the annular conduit 48 through the gold 50 and a hole 51 in the housing 28. One or more arranged between the first pressure plate 32 and the second pressure plate 44 The spiral spring returns the hydraulic piston 46 to the initial position after braking.   Each of the first pressure plate 32 and the second pressure plate 44 and the friction disc 36 and the disk plate 40 are preferably annular, but they also It can be arranged in a circular section around the center line 15 of the carrier 2.   According to the first embodiment shown in FIG. Self-adjusting member 5 for adjusting the initial position of the hydraulic piston 46 due to wear of the 2 are optionally provided. The self-adjusting member 52 is closed on one side in the housing 28. It consists of a sleeve 53 arranged with a grip fitted in the obturator 54. Said Three One pin 56 extending through the valve 53 has a hydraulic piston 46 at a first end 58. At the second end 60, the pin is provided with a head 62, The bearing 62 has a bearing surface 64 for pressing against an end surface 66 of the sleeve 53. Having. Since the friction disc 36 is worn, the friction disc 36 and the To compress the disk plate 40 against the first pressure plate 32, the hydraulic piston 46 must travel a longer distance, resulting in a greater amount of hydraulic fluid Is required. To overcome this problem, act on the hydraulic piston 46 The force from the hydraulic fluid is applied to the sleeve 53 using the head 62 of the pin 56. The sleeve 53 is displaced in the one-side closing hole 54 so as to occupy a new position. The grip between the one-side obstruction 54 is adapted. However, the spiral spring G 49 so that the sleeve 53 does not displace the sleeve 53 in the one-side closing hole 54. The grip between the sleeve 53 and the one-side obstruction hole 54 is adapted, Meaning that the hydraulic piston 46 occupies a new initial position after the return stroke I have.   One option is that the sensors 68 are also arranged in the housing 18. The sensor also senses the vehicle speed by sensing the rotational speed of the planet carrier 2. The sensor 68 is appropriately located in the hole 70 of the housing 28 with the first pressure plate 32. Arrayed, said sensors pointing at splines 38 on the periphery of the planet carrier 2; The first friction disks 36 are arranged on the splines. Then, The sensor 68 determines how fast the bar of the spline 38 passes through the sensor 68. And its speed is proportional to the rotation speed of the planet carrier 2. The sensor 6 8, the first friction disc 36 is provided on the planet carrier 2. Teeth or splines at finer intervals next to the splines 38 where It can be provided selectively.   FIG. 2 shows a second embodiment according to the present invention. The play according to the second embodiment The star transmission is engaged with the splines 42 formed in the housing 28. One outer gear ring 30 'is arranged. The height of the spline 42 is In the part interacting with the gear ring 30 ', one lock for the gear ring 30' Or reduced to form a bearing surface. The outer gear ring 30 'has a Engage with splines 42 within housing 28 to form a two spline connection Supra An in 74 is disposed on the outer perimeter.   The gear ring 30 'forms the friction disc 36 and the friction brake 34. One first pressure plate 32 'for the disk plate 40 is formed. The friction The brake 34 is connected to the fluid circulated through a cooling device (not shown) using the pipe 72. It is preferable to operate in this case.   FIG. 2 shows a self-adjusting member 52 '. This self-adjusting member 52 ' The initial position of the hydraulic piston 46 'is adjusted because the friction disk 36 is worn. Figure Apart from the above features relating to 2, the configuration of the part of the planetary transmission according to FIG. Essentially, it corresponds to the configuration of the parts described in connection with the planetary transmission of FIG.

───────────────────────────────────────────────────── フロントページの続き (81)指定国 ＥＰ(ＡＴ，ＢＥ，ＣＨ，ＣＹ， ＤＥ，ＤＫ，ＥＳ，ＦＩ，ＦＲ，ＧＢ，ＧＲ，ＩＥ，Ｉ Ｔ，ＬＵ，ＭＣ，ＮＬ，ＰＴ，ＳＥ)，ＯＡ(ＢＦ，ＢＪ ，ＣＦ，ＣＧ，ＣＩ，ＣＭ，ＧＡ，ＧＮ，ＭＬ，ＭＲ， ＮＥ，ＳＮ，ＴＤ，ＴＧ)，ＡＰ(ＧＨ，ＧＭ，ＫＥ，Ｌ Ｓ，ＭＷ，ＳＤ，ＳＺ，ＵＧ，ＺＷ)，ＥＡ(ＡＭ，ＡＺ ，ＢＹ，ＫＧ，ＫＺ，ＭＤ，ＲＵ，ＴＪ，ＴＭ)，ＡＬ ，ＡＭ，ＡＴ，ＡＵ，ＡＺ，ＢＡ，ＢＢ，ＢＧ，ＢＲ， ＢＹ，ＣＡ，ＣＨ，ＣＮ，ＣＵ，ＣＺ，ＤＥ，ＤＫ，Ｅ Ｅ，ＥＳ，ＦＩ，ＧＢ，ＧＥ，ＧＨ，ＧＭ，ＧＷ，ＨＵ ，ＩＤ，ＩＬ，ＩＳ，ＪＰ，ＫＥ，ＫＧ，ＫＰ，ＫＲ， ＫＺ，ＬＣ，ＬＫ，ＬＲ，ＬＳ，ＬＴ，ＬＵ，ＬＶ，Ｍ Ｄ，ＭＧ，ＭＫ，ＭＮ，ＭＷ，ＭＸ，ＮＯ，ＮＺ，ＰＬ ，ＰＴ，ＲＯ，ＲＵ，ＳＤ，ＳＥ，ＳＧ，ＳＩ，ＳＫ， ＳＬ，ＴＪ，ＴＭ，ＴＲ，ＴＴ，ＵＡ，ＵＧ，ＵＳ，Ｕ Ｚ，ＶＮ，ＹＵ，ＺＷ────────────────────────────────────────────────── ─── Continuation of front page    (81) Designated country EP (AT, BE, CH, CY, DE, DK, ES, FI, FR, GB, GR, IE, I T, LU, MC, NL, PT, SE), OA (BF, BJ , CF, CG, CI, CM, GA, GN, ML, MR, NE, SN, TD, TG), AP (GH, GM, KE, L S, MW, SD, SZ, UG, ZW), EA (AM, AZ , BY, KG, KZ, MD, RU, TJ, TM), AL , AM, AT, AU, AZ, BA, BB, BG, BR, BY, CA, CH, CN, CU, CZ, DE, DK, E E, ES, FI, GB, GE, GH, GM, GW, HU , ID, IL, IS, JP, KE, KG, KP, KR, KZ, LC, LK, LR, LS, LT, LU, LV, M D, MG, MK, MN, MW, MX, NO, NZ, PL , PT, RO, RU, SD, SE, SG, SI, SK, SL, TJ, TM, TR, TT, UA, UG, US, U Z, VN, YU, ZW

Claims (1)

【特許請求の範囲】 １．少なくとも１つの遊星歯車（４）が装着される遊星キャリヤ（２）、車両用 の車輪（２５）のために配列され、前記遊星キャリヤ（２）に接続されるハブ（ １６）、車両に接続され、内部には前記ハブ（１６）が装着される静的ハウジン グ（２８）、および前記遊星キャリヤ（２）の外周縁部に配列され、前記静的ハ ウジング（２８）に関連して前記遊星キャリヤ(２)の回転の制動を行うことにあ る摩擦ブレーキ(３４)から成る車両用の遊星変速装置において、前記ハブ（１６ ）と前記遊星キャリヤ（２）が第１スプライン接続（１４，２１）によって内部 結合されることを特徴とする遊星変速装置。 ２．遊星キャリヤ（２）がスプライン孔１２から成り、該スプライン孔（１２） の中央線（１５）が遊星キャリヤ（２）の回転軸に一致していることと、前記ハ ブ（１６）が遊星キャリヤ（２）の前記スプライン孔（１２）内に配列されるス プラインジャーナル（２０）から成ることとを特徴とする請求項１記載の遊星変 速装置。 ３．前記ハブ（１６）の前記スプラインジャーナル（２０）が該ハブ（１６）の 第１端部（１８）に配列される１枚の板（１９）を使い遊星キャリヤ（２）の前 記スプライン孔（１２）内で軸方向に固定されることを特徴とする請求項２記載 の遊星変速装置。 ４．前記摩擦ブレーキ（３４）が遊星キャリヤ（２）の周縁部上に配列される第 １摩擦ディスク（３６）の集合と静的ハウジング（２８）の内側に配列される第 ２の摩擦ディスク（４０）の集合とから成ることを特徴とする請求項１から３の 中のいずれか１つに記載の遊星変速装置。 ５．前記第１と第２の摩擦ディスク（それぞれ、３６と４０）が遊星キャリヤ（ ２９）と静的ハウジング（２８）上でそれぞれ軸方向に変位可能であることを特 徴とする請求項４記載の遊星変速装置。 ６．前記摩擦ブレーキ（３４）のための１枚の第１圧力板（３２，３２’）が静 的ハウジング（２８）上に配列されることと、１枚の第２圧力板（４４）が制動 の際に前記第１圧力板（３２）の方向に変位し、前記第１と第２圧力板（３２， ４４）の間の前記第１および第２摩擦ディスク（それぞれ３６と４０）を圧縮す るように配列されることとを特徴とする請求項５記載の遊星変速装置。 ７．少なくとも１つの油圧ピストン（４６、４６’）が静的ハウジング（２８） 内に配列され、制動の際に、前記第２圧力板（４４）を前記第１圧力板（３２） の方向に変位させることを特徴する請求項６記載の遊星変速装置。 ８．環状導管（４８）が静的ハウジング（２８）内に配列され、油圧流体を含み 得ることと、該環状導管（４８）が少なくとも１つの油圧シリンダ（４６、４６ ’）に対して流体接続を有することとを特徴とする請求項７記載の遊星変速装置 。 ９．少なくとも１つの油圧シリンダ（４６、４６’）が、スリーブ（５３）を経 由して、静的ハウジング（２８）の穴（５４）の中で変位可能に配列される自己 調整部材（５２）から成り、該スリーブ（５３）内で軸方向に移動可能なピン（ ５６）は前記油圧ピストン（４６、４６’）に接続されることを特徴とする請求 項７或は８記載の遊星変速装置。 １０．外側歯車環（３０，３０’）が静的ハウジング（２８）上に配列されるこ とと、内側太陽歯車（１０）が車両の駆動シャフト（６）上に配列されることと を特徴とする請求項１から９の中のいずれか１つに記載の遊星変速装置。 １１．外側歯車環（３０，３０’）が前記第１圧力板（３２，３２’）上に配列 されることを特徴とする請求項６から９の中のいずれか１つに記載の遊星変速装 置。 １２．前記外側歯車環（３０’）が第２スプライン接続（４２，７４）によって 静的ハウジング（２８）に接続されることを特徴とする請求項１０或は１１記載 の遊 星変速装置。 １３．静的ハウジング（２８）内に配列されるヤンサ（６８）が、遊星キャリヤ （２）の周縁部上の表面と相互作用し、この方法を通して遊星キャリア（２）の 回転速度を感知するように適合されることを特徴とする請求項１から１２の中の いずれか１つに記載の遊星変速装置。 １４．少なくとも１つの遊星歯車（４）が装着される遊星キャリヤ（２）、車両 用の車輪（２５）のために配列され、前記遊星キャリヤ（２）に接続されるハブ （１６）、車両に接続され、内部には前記ハブ（１６）が装着される静的ハウジ ング（２８）、および前記遊星キャリヤ（２）の外周縁部に配列され、前記静的 ハウジング（２８）に関連し前記遊星キャリヤ（２）の回転の制動を行うことに ある摩擦ブレーキ（３４）から成る車両用の遊星変速装置において、１つの外側 歯車環（３０’）が少なくとも１つの遊星歯車（４）と相互作用するように配列 されることと、該外側歯車環（３０’）が第２スプライン接合（４２，７４）に よって静的ハウジング（２８）に接続されることとを特徴とする遊星変速装置。 １５．スプライン（７４）が前記外側歯車環（３０’）の外側周縁部上に配設さ れることと、スプライン（４２）がハウジング内（２８）に配列され、該スプラ イン（４２，７４）が第２スプライン接続（４２，７４）を形成することとを特 徴とする請求項１４記載の遊星変速装置。 １６．前記摩擦ブレーキ（３４）が遊星キャリア（２）の周縁部上に配列される 第１摩擦ディスク（３６）の集合と、静的ハウジング（２８）内で前記スプライ ン（４２）と係合するように配列される第２摩擦ディスク（４０）であって、静 的ハウジング（２８）の内側に配列される該第２摩擦ディスク（４０）の集合と から成ることを特徴とする請求項１４或は１５記載の遊星変速装置。 １７．前記外側歯車環（３０’）が、制動の際、前記第１と第２摩擦ディスク（ ３ ６，４０）を圧縮するように配列される１枚の第１圧力板（３２’）を形成する ことを特徴とする請求項１６記載の遊星変速装置。[Claims] 1. Planetary carrier (2) to which at least one planetary gear (4) is mounted, for vehicles Hub (25) arranged for the wheels (25) and connected to said planet carrier (2) 16) a static housing connected to the vehicle and having the hub (16) mounted therein (28) and the outer periphery of the planet carrier (2), Braking the rotation of the planet carrier (2) in connection with the housing (28); A planetary transmission for a vehicle comprising a friction brake (34), ) And said planet carrier (2) are internally connected by a first spline connection (14, 21). A planetary transmission characterized by being coupled. 2. The planet carrier (2) comprises a spline hole 12; Center line (15) coincides with the rotation axis of the planet carrier (2); The gears (16) are arranged in the spline holes (12) of the planet carrier (2). 2. The planetary gear according to claim 1, wherein said planetary gear comprises a pline journal. Speed device. 3. The spline journal (20) of the hub (16) is In front of the planet carrier (2) using one plate (19) arranged at the first end (18) 3. The spline hole according to claim 2, wherein said spline hole is axially fixed in said spline hole. Planetary transmission. 4. A third friction brake (34) arranged on the periphery of the planet carrier (2); A set of friction disks (36) and a second array arranged inside a static housing (28). And a set of two friction disks (40). The planetary transmission according to any one of the above. 5. The first and second friction disks (36 and 40, respectively) are connected to a planet carrier ( 29) and that it is axially displaceable on the static housing (28). The planetary transmission according to claim 4, wherein 6. One first pressure plate (32, 32 ') for the friction brake (34) is static. Being arranged on the dynamic housing (28) and one second pressure plate (44) being braked At this time, the first and second pressure plates (32, 32) are displaced in the direction of the first pressure plate (32). 44) compressing said first and second friction discs (36 and 40 respectively) The planetary transmission according to claim 5, wherein the planetary transmission is arranged in such a manner as to be arranged as follows. 7. The at least one hydraulic piston (46, 46 ') has a static housing (28). And when braking, the second pressure plate (44) is connected to the first pressure plate (32). 7. The planetary transmission according to claim 6, wherein the planetary transmission is displaced in the direction of. 8. An annular conduit (48) is arranged within the static housing (28) and contains hydraulic fluid. And that said annular conduit (48) has at least one hydraulic cylinder (46, 46). 8. The planetary transmission according to claim 7, wherein the planetary transmission has a fluid connection to the planetary gear. . 9. At least one hydraulic cylinder (46, 46 ') passes through a sleeve (53). The self-displaceable arrangement in the hole (54) of the static housing (28) A pin (52) consisting of an adjusting member (52) and axially movable within said sleeve (53); 56) is connected to said hydraulic piston (46, 46 '). Item 9. The planetary transmission according to item 7 or 8. 10. The outer gear ring (30, 30 ') is arranged on the static housing (28). And that the inner sun gear (10) is arranged on the drive shaft (6) of the vehicle; The planetary transmission according to any one of claims 1 to 9, characterized in that: 11. Outer gear ring (30, 30 ') is arranged on said first pressure plate (32, 32') The planetary transmission according to any one of claims 6 to 9, wherein Place. 12. The outer gear ring (30 ') is connected by a second spline connection (42, 74). 12. The static housing (28) connected to a static housing (28). Play Star transmission. 13. A yansa (68) arranged in a static housing (28) is provided with a planet carrier. Interacts with the surface on the periphery of (2) and through this method the planetary carrier (2) 13. The method according to claim 1, wherein the sensor is adapted to sense a rotational speed. A planetary transmission according to any one of the preceding claims. 14． Planetary carrier (2), vehicle with at least one planetary gear (4) mounted Hub arranged for wheels (25) and connected to said planet carrier (2) (16) A static housing connected to a vehicle and having the hub (16) mounted therein. (28) and the outer periphery of the planet carrier (2), Braking the rotation of said planet carrier (2) in relation to the housing (28); In a planetary transmission for a vehicle comprising a friction brake (34), one outer A gear ring (30 ') arranged to interact with at least one planetary gear (4) And the outer gear ring (30 ') is connected to the second spline joint (42, 74). Therefore, the planetary transmission is connected to the static housing (28). 15. A spline (74) is disposed on the outer periphery of said outer gear ring (30 '). The splines (42) are arranged in the housing (28), In (42, 74) forming a second spline connection (42, 74). 15. The planetary transmission according to claim 14, wherein: 16. The friction brake (34) is arranged on the periphery of the planet carrier (2) An assembly of a first friction disc (36) and said splice in a static housing (28). A second friction disc (40) arranged to engage with the A collection of said second friction discs (40) arranged inside a dynamic housing (28); 16. The planetary transmission according to claim 14, wherein the transmission comprises: 17． When the outer gear ring (30 ') brakes, the first and second friction disks (30') 3 6, 40) to form one first pressure plate (32 ') arranged to compress. 17. The planetary transmission according to claim 16, wherein:
JP11506997A 1997-07-18 1998-05-12 Planetary transmission for vehicles Pending JP2001500823A (en)

Applications Claiming Priority (3)

Application Number Priority Date Filing Date Title
SE9702749A SE509788C2 (en) 1997-07-18 1997-07-18 Planetary gear for a vehicle wheel
SE9702749-4 1997-07-18
PCT/SE1998/000865 WO1999003699A1 (en) 1997-07-18 1998-05-12 Planetary transmission for a vehicle

Publications (2)

Publication Number Publication Date
JP2001500823A true JP2001500823A (en) 2001-01-23
JP2001500823A5 JP2001500823A5 (en) 2004-10-14

Family

ID=20407781

Family Applications (1)

Application Number Title Priority Date Filing Date
JP11506997A Pending JP2001500823A (en) 1997-07-18 1998-05-12 Planetary transmission for vehicles

Country Status (11)

Country Link
US (2) USRE41285E1 (en)
EP (3) EP1354747B1 (en)
JP (1) JP2001500823A (en)
KR (1) KR100498819B1 (en)
CN (1) CN1234775A (en)
AU (1) AU744108C (en)
BR (1) BR9806029A (en)
DE (3) DE69830011T2 (en)
NO (1) NO316572B1 (en)
SE (1) SE509788C2 (en)
WO (1) WO1999003699A1 (en)

Cited By (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JP2007120649A (en) * 2005-10-28 2007-05-17 Komatsu Ltd Axle device and working machine
WO2014155836A1 (en) * 2013-03-29 2014-10-02 株式会社小松製作所 Axle device for working vehicle, and working vehicle

Families Citing this family (35)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE19718744C1 (en) 1997-05-02 1998-11-19 Zahnradfabrik Friedrichshafen Vehicle transmission with integrated brake
US6616567B2 (en) 2000-10-10 2003-09-09 Terex Corporation Two speed gear box
CA2350263C (en) * 2001-06-12 2006-09-05 Dt Planetaries Inc. Multi-speed wheel hub for automotive vehicles
US6550588B2 (en) * 2001-07-10 2003-04-22 Caterpillar Inc Off highway truck brake assembly and wheel spindle having a spline joint
SE523652C2 (en) * 2001-11-08 2004-05-04 Volvo Constr Equip Components Annular means for a braking device and a device for driving a wheel of a vehicle comprising said annular means
SE523111C2 (en) * 2001-11-08 2004-03-30 Volvo Constr Equip Components Device for driving a wheel of a vehicle
SE525626C2 (en) * 2003-03-05 2005-03-22 Volvo Constr Equip Holding Se Device for driving a wheel of a vehicle
DE10326139A1 (en) 2003-06-06 2005-01-13 Zf Friedrichshafen Ag Drives for mobile vehicles
DE10326143A1 (en) 2003-06-06 2004-12-23 Zf Friedrichshafen Ag Drive for a mobile vehicle
US6890282B2 (en) * 2003-06-11 2005-05-10 Zf Friedrichshafen Ag Driveline for mobile vehicles
US6869380B2 (en) * 2003-06-11 2005-03-22 Zf Friedrichshafen Ag Driveline for mobile-vehicles
SE0302568L (en) * 2003-09-26 2004-10-12 Volvo Constr Equip Holding Se Device for driving a wheel of a vehicle, as well as a planet carrier
DE102004013301B4 (en) * 2004-03-18 2020-11-05 Zf Friedrichshafen Ag Multi-disc brake for a vehicle transmission
US20050252730A1 (en) * 2004-05-14 2005-11-17 Ernst Auer Wheel hub
SE527256C2 (en) 2004-06-30 2006-01-31 Volvo Constr Equip Holding Se Planetary transmission, drive including the planetary transmission and brake lamella for the planetary transmission
US8083634B2 (en) * 2005-06-27 2011-12-27 Volvo Construction Equipment Ab Disk brake, planet transmission, drive device and work vehicle
EP1910121B1 (en) * 2005-07-01 2012-09-12 Volvo Construction Equipment AB Planet transmission, drive device comprising the planet transmission and vehicle comprising the drive device
US8256583B2 (en) * 2007-04-20 2012-09-04 Deere & Company Integrated outboard wet disk brake
CN100516590C (en) * 2007-08-08 2009-07-22 绍兴前进齿轮箱有限公司 Gear box with built-in braking system
US8340880B2 (en) * 2007-08-28 2012-12-25 Lockheed Martin Corporation System and method for automatically and independently controlling wheel torque or speed using wheel hubs having engagement/disengagement mechanisms integrated therewith
US20130012350A1 (en) * 2010-02-12 2013-01-10 Magna Powertrain Ag Wheel hub drive for motor vehicles
US8534431B2 (en) 2010-07-21 2013-09-17 Warn Industries, Inc. Face tooth hydraulic piston brake
DE102012208920A1 (en) * 2012-05-29 2013-12-05 Zf Friedrichshafen Ag Wheel head for axle of e.g. wheeled loader, has wheel gear drivingly connected with shaft end at driving end, where shaft end forms connector socket that is rotatably inserted into drive shaft for coupling wheel hub gear box
DE102012208921A1 (en) * 2012-05-29 2013-12-05 Zf Friedrichshafen Ag Wheel head for shaft of work vehicle, has brake disc pack that is set against stop surface formed on brake housing facing side of flange portion
WO2014063729A1 (en) * 2012-10-24 2014-05-01 Zollern Gmbh & Co.Kg Final drive unit with brake
JP6170321B2 (en) * 2013-03-29 2017-07-26 住友重機械工業株式会社 Excavator
CN104358804B (en) * 2014-10-29 2017-03-01 李开卫 Multi-sheet wet-type disk brake and its operation method
ES2716083T3 (en) * 2014-11-07 2019-06-10 Comer Ind Spa Epicycloidal reduction unit for applications with an ascending output
DE102014018485B3 (en) 2014-12-16 2015-09-17 Sew-Eurodrive Gmbh & Co Kg Electromagnetically actuated brake device
US9939056B2 (en) 2015-10-20 2018-04-10 Caterpillar Inc. Final drive system for a machine
EP3439907B1 (en) * 2016-04-05 2021-12-01 Volvo Construction Equipment AB A planet carrier and a planetary gear transmission
CN106286648B (en) * 2016-11-09 2019-02-19 广西柳工机械股份有限公司 Brake for hydrostatic transmissions
DE102018107850A1 (en) * 2017-04-05 2018-10-11 Borgwarner Inc., Patent Department The torque transfer device
CN107284226A (en) * 2017-06-26 2017-10-24 洛阳舒诚机械设备有限公司 A kind of self-driven wheel of electric flatbed tricycle
CN109027055A (en) * 2018-07-11 2018-12-18 中国煤炭科工集团太原研究院有限公司 One kind being used for the totally-enclosed actuating unit of the electronic rubber-tired cart of coal mine explosion-proof

Family Cites Families (56)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US2776583A (en) 1954-04-05 1957-01-08 Rockwell Spring & Axle Co Drive mechanism for crop harvesting vehicles
US2920722A (en) 1958-02-12 1960-01-12 Gen Motors Corp Brake-adjusting device
US2998735A (en) * 1959-04-15 1961-09-05 Massey Ferguson Inc Drive axle gearing assembly
US3115204A (en) * 1960-11-16 1963-12-24 Clark Equipment Co Power wheel assembly
US3092370A (en) * 1961-11-22 1963-06-04 Superior Equipment Company Winch unit
DE2124009C3 (en) * 1971-05-14 1980-02-21 Zf Getriebe Gmbh, 6600 Saarbruecken Planetary gear carrier made from sheet metal parts for a planetary gear unit
US3754625A (en) 1972-06-07 1973-08-28 Allis Chalmers Vehicle final drive with planetary gearing and friction brake
DE2357451C2 (en) 1973-11-17 1981-09-24 Carl Hurth Maschinen- und Zahnradfabrik GmbH & Co, 8000 München Wheel hub drive with brake
GB1464101A (en) 1974-05-08 1977-02-09 Hine M Vehicles
US3957146A (en) * 1975-02-19 1976-05-18 The B. F. Goodrich Company Automatic adjuster with cutter for friction couplings
US4181042A (en) 1976-12-13 1980-01-01 Trw Inc. Drive assembly
US4173269A (en) 1978-02-23 1979-11-06 Clark Equipment Company Wet brake or clutch
GB2043186A (en) 1979-02-15 1980-10-01 Newton Transmissions Ltd Oil immersed brake, bearing pump
JPS57104410A (en) 1980-12-22 1982-06-29 Toyo Umpanki Co Ltd Driving shaft device
GB2122146A (en) 1982-06-10 1984-01-11 Newage Transmissions Limited Axles
DE3222261A1 (en) 1982-06-10 1983-12-15 Mannesmann AG, 4000 Düsseldorf Brake for heavy vehicles
US4611506A (en) * 1983-04-29 1986-09-16 Clark Equipment Company Hydraulically actuated planetary wheel drive
US4649772A (en) * 1985-07-05 1987-03-17 Caterpillar Inc. Planetary wheel drive assembly
US4662246A (en) * 1985-10-03 1987-05-05 Caterpillar Inc. Multistage planetary final drive mechanism
US4655326A (en) 1985-11-29 1987-04-07 Dana Corporation Cooling system for planetary wheel end with wet brake
US4646880A (en) 1985-11-29 1987-03-03 Dana Corporation Planetary wheel end with wet brake
EP0324768B1 (en) * 1986-09-30 1990-09-19 ZF FRIEDRICHSHAFEN Aktiengesellschaft Liquid-cooled friction brake
HU203704B (en) 1987-09-28 1991-09-30 Magyar Vagon Es Gepgyar Epicyclic-gear carriage
US5024636A (en) 1989-06-27 1991-06-18 Fairfield Manufacturing Company, Inc. Planetary wheel hub
JP2769323B2 (en) * 1988-06-29 1998-06-25 アイシン・エィ・ダブリュ株式会社 Motor drive device with reduction gear and electric vehicle
DE3836457A1 (en) 1988-10-26 1990-05-03 Fendt & Co Xaver Torque transmission unit
DE3900075A1 (en) * 1989-01-03 1990-07-12 Magyar Vagon Es Gepgyar WHEEL HEAD FOR VEHICLES
DE3905292A1 (en) 1989-02-21 1990-08-23 Linde Ag Wheel-drive unit
DE4011022A1 (en) 1989-04-08 1990-10-11 Zahnradfabrik Friedrichshafen Drive axle joining transmission and wheel hub - uses circulating fluid to cool multi-plate brakes
US5147255A (en) * 1990-04-03 1992-09-15 Hurth Getriebe Und Zahnraeder G.M.B.H. Spur gear transmission, in particular for a drive unit of an industrial truck
DE4011304C1 (en) * 1990-04-07 1991-08-01 Carl Hurth Maschinen- Und Zahnradfabrik Gmbh & Co, 8000 Muenchen, De Multi-disc vehicle brake - is actuated by two-arm lever fitted outside gear housing, one arm acting on pedal and other on axial pressure plate
US5064530A (en) 1990-06-04 1991-11-12 Caterpillar Inc. Fluid contamination detecting apparatus
JPH0446237A (en) 1990-06-12 1992-02-17 Yoichi Tatara Nonlinear type elastic supporting body utilizing rubber sphere
FR2667374B1 (en) 1990-09-27 1995-02-10 Peugeot DEVICE FOR TRANSMITTING A DRIVE TORQUE OF A MOTOR VEHICLE WHEEL WITH A BEARING AND A SPEED REDUCER INTEGRATED INTO THE WHEEL.
DE9111129U1 (en) 1991-09-07 1993-01-14 Keßler & Co GmbH, 7083 Abtsgmünd Two-stage planetary gear
US5228543A (en) * 1992-02-03 1993-07-20 Power Transmission Technology, Inc. Sealed wet disc brake for vehicles
DE4206101C2 (en) 1992-02-27 1997-11-06 Linde Ag Hydromechanical drive system
DE4206087C2 (en) 1992-02-27 1994-01-27 Linde Ag Hydromechanical wheel drive
DE4206100B4 (en) 1992-02-27 2004-09-16 Linde Ag Switchable planetary gear
BR9202976A (en) 1992-07-31 1994-02-01 Rockwell Braseixos Sa PLANETARY REDUCTION FOR DRIVING AXLES
JP3104819B2 (en) 1992-09-24 2000-10-30 株式会社豊田自動織機製作所 Wet disc brake
US5522259A (en) 1992-11-26 1996-06-04 O&K Orenstein & Koppel Ag Process and arrangement for measuring multiple disk brake wear
DE4338468C2 (en) 1992-11-26 1996-01-25 Orenstein & Koppel Ag Method and device for measuring wear on multi-disc brakes
DE4300445C2 (en) 1993-01-09 2003-04-24 Linde Ag Self-supporting truck drive axle
US5397282A (en) * 1993-09-07 1995-03-14 Weidman; William A. Two-speed planetary final drive system with self-timed freewheeler shifts
US5476272A (en) * 1994-01-19 1995-12-19 Federal-Mogul Corporation Speed sensor ring for vehicle anti-lock brake system
DE4439360C2 (en) 1994-07-13 1998-02-26 Orenstein & Koppel Ag Device for at least partially overcoming or canceling the gear play in a braked construction and working machine working in the state
DE4433100C2 (en) 1994-09-16 1998-10-15 Zf Hurth Gotha Gmbh Gearbox with integrated brake, in particular for a drive unit of an industrial truck
US5509864A (en) 1994-12-22 1996-04-23 General Motors Corporation Split ring axial positioner for planetary gear assembly
JPH08177992A (en) 1994-12-28 1996-07-12 Jatco Corp Carrier coupling structure of automatic transmission
DE19500765A1 (en) 1995-01-13 1996-07-25 Orenstein & Koppel Ag Method and device for readjusting a multi-disc brake, especially in oil
US5645148A (en) * 1995-06-23 1997-07-08 Zf Padova S.P.A. Transmission with built-in brake, particularly for vehicles
JP3722451B2 (en) 1996-06-26 2005-11-30 株式会社小松製作所 Self-propelled vehicle
DE19640146C1 (en) 1996-09-28 1998-01-08 Orenstein & Koppel Ag Wheel hub with integrated planetary step and outer brake for axles
US5842947A (en) * 1996-12-31 1998-12-01 Borg-Warner Automotive, Inc. Planetary gear carrier having a band brake on an axial extension of the carrier for transfer cases
DE19718744C1 (en) 1997-05-02 1998-11-19 Zahnradfabrik Friedrichshafen Vehicle transmission with integrated brake

Cited By (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JP2007120649A (en) * 2005-10-28 2007-05-17 Komatsu Ltd Axle device and working machine
WO2014155836A1 (en) * 2013-03-29 2014-10-02 株式会社小松製作所 Axle device for working vehicle, and working vehicle
JP2014193694A (en) * 2013-03-29 2014-10-09 Komatsu Ltd Axle device of work vehicle and work vehicle

Also Published As

Publication number Publication date
SE509788C2 (en) 1999-03-08
DE69818960T2 (en) 2004-07-29
USRE41285E1 (en) 2010-04-27
DE69830011T2 (en) 2006-03-09
AU7463598A (en) 1999-02-10
EP0928253A1 (en) 1999-07-14
EP1354747A2 (en) 2003-10-22
US6090006A (en) 2000-07-18
EP1258381A3 (en) 2003-12-10
DE69818960D1 (en) 2003-11-20
SE9702749L (en) 1999-01-19
DE69834962D1 (en) 2006-07-27
CN1234775A (en) 1999-11-10
BR9806029A (en) 2000-01-18
WO1999003699A1 (en) 1999-01-28
AU744108C (en) 2004-03-04
KR20000068589A (en) 2000-11-25
EP1258381B1 (en) 2005-04-27
NO990830L (en) 1999-02-22
NO990830D0 (en) 1999-02-22
EP0928253B1 (en) 2003-10-15
DE69830011D1 (en) 2005-06-02
EP1258381A2 (en) 2002-11-20
EP1354747A3 (en) 2003-12-10
NO316572B1 (en) 2004-02-23
EP1354747B1 (en) 2006-06-14
KR100498819B1 (en) 2005-07-01
SE9702749D0 (en) 1997-07-18
DE69834962T2 (en) 2007-01-25
AU744108B2 (en) 2002-02-14

Similar Documents

Publication Publication Date Title
JP2001500823A (en) Planetary transmission for vehicles
EP1763448B1 (en) Planet transmission and drive device comprising the planet transmission
US8376091B2 (en) Floating-disk type brake system
KR20050008824A (en) Cone disc infinitely-variable gearbox
CN103448536B (en) The axletree of wheel rim and working truck for the axletree of working truck
EP1446303B1 (en) An arrangement for driving a wheel of a vehicle
US6508734B2 (en) Differential lock actuator
US5906249A (en) Drive system of a drive wheel
US8066605B2 (en) Planet transmission, drive device comprising the planet transmission and vehicle comprising the drive device
EP1446591B1 (en) Arrangement for driving a wheel of a vehicle which comprises an annular member for a braking device
US4874064A (en) Brake apparatus for automotive vehicle
EP1899619B1 (en) Planetary transmission, drive device and work vehicle
US5794751A (en) Piston for torque transmitting systems
US6536560B1 (en) Single braking assembly for a drive axle
EP1132270A2 (en) Wheel hub for vehicles
AU762590B2 (en) Planetary transmission for a vehicle
US4923040A (en) High torque brake/lock differential with equal torque split capability
US6332523B1 (en) Axle assembly parking brake mechanism
JP3101046B2 (en) Planetary gear differential
JP2750284B2 (en) Brake devices in automobiles
JP2646161B2 (en) Steering brake device for self-propelled working machine
JPH09317800A (en) Brake device

Legal Events

Date Code Title Description
A131 Notification of reasons for refusal

Free format text: JAPANESE INTERMEDIATE CODE: A131

Effective date: 20060328

A521 Request for written amendment filed

Free format text: JAPANESE INTERMEDIATE CODE: A523

Effective date: 20060627

A02 Decision of refusal

Free format text: JAPANESE INTERMEDIATE CODE: A02

Effective date: 20061031